Compact rotary compressor

ABSTRACT

A compact rotary compressor having a motor with a stator and a rotor wherein the rotor includes an integrally formed part defining an internal compression chamber and an integrally formed vane extending radially inwardly within the compression chamber. A roller is rotatably mounted and eccentrically disposed within the compression chamber with the vane being engaged with the roller whereby rotation of the rotor also rotates the roller. The rotor and roller may each be mounted on a stationary shaft. End plates located on the opposite axial ends of the rotor seal the compression chamber and one of the ends plates may be rotatably mounted on a stationary support structure. One of the end plates may also include a discharge valve assembly and noise attenuation chamber as part of a discharge fluid line providing communication between the compression chamber and a passageway located within the stationary shaft.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to a rotary compressor having a compactdesign wherein the compression chamber is defined by the rotor of themotor driving the compressor.

2. Description of the Related Art

Rotary compressors typically include a housing in which a motor and acompression mechanism are mounted being operably connected by a driveshaft. Rotary type compression mechanisms typically include a rollerdisposed about an eccentric portion of a shaft. The roller is located ina cylinder block that defines a cylindrical compression space. At leastone vane extends between the roller and the outer wall of thecompression chamber to divide the compression chamber into a pluralityof compression pockets. The roller is eccentrically located within thecompression chamber and, as the shaft rotates, the compression pocketsbecome progressively smaller thereby compressing a refrigerant or otherfluid disposed therein. Oftentimes, the vane is biased into contact witheither the wall of the compression chamber or the roller by a spring.Other configurations of rotary compressors are also known.

SUMMARY OF THE INVENTION

The present invention provides a compact rotary compressor in which therotor of the motor includes a single integral part that also defines aninternal compression chamber and includes an integrally formed vaneextending radially inwardly into the compression chamber.

The present invention comprises, in one form thereof, a rotarycompressor for compressing a fluid that includes a motor having a statorand a rotor. The rotor includes an integrally formed part defining aninternal compression chamber and an integrally formed vane extendingradially inwardly within the compression chamber. A roller is rotatablymounted and eccentrically disposed within the compression chamber. Thevane is engaged with the roller wherein rotation of the rotor rotatesthe roller and thereby compresses the fluid within the compressionchamber.

The integrally formed rotor part may also include a radially outersurface having a plurality of permanent magnets mounted thereon.Further, the roller may define a recess having a bushing mountedtherein, wherein the bushing defines a radially extending slot with thevane being slidably disposed within the slot. The roller may be mountedon a stationary shaft wherein the shaft defines an internal passagewayin fluid communication with the compression chamber.

The compressor may also include first and second end plates disposed atopposite axial ends of the compression chamber. At least one of the endplates may define a fluid passageway providing fluid communicationbetween the internal passageway of the shaft and the compressionchamber. The shaft extends through one of the end plates. In someembodiments, the shaft may extend through only one of the end plates andwith the other end plate being rotatably mounted on a stationary supportstructure. The stator circumscribes the rotor, the compression chamberdisposed therein and the first and second end plates.

One of the end plates disposed at an end of the compression chamber maydefine a discharge fluid line having a discharge valve cavity in fluidcommunication with the compression chamber and a discharge valve memberdisposed within the discharge valve cavity and controlling fluid flowfrom the compression chamber through the discharge valve cavity. The endplate may also further define a noise attenuation chamber in fluidcommunication with the discharge fluid line.

The present invention comprises, in another form thereof, a rotarycompressor for compressing a fluid that includes a housing and a motormounted in the housing. The motor has a stator and a rotor with thestator circumscribing the rotor. The rotor defines a rotational axis andincludes an integrally formed part defining an internal compressionchamber and an integrally formed vane extending radially inwardly withinsaid compression chamber. Opposite axial ends of the rotor define firstand second rotor faces respectively. A first end plate is secured to thefirst rotor face and a second end plate is secured to the second rotorface. A stationary shaft is mounted in the housing and extends throughat least one of the end plates and is at least partially disposed withinthe compression chamber. A roller is rotatably mounted on the shafteccentric wherein the roller is rotatable about an axis spaced from therotational axis of the rotor. The vane is engaged with the rollerwherein rotation of the rotor rotates the roller on the shaft andthereby compresses the fluid within the compression chamber.

An advantage of the present invention is that it provides a compactrotary compressor having relatively high reliability with reducedvibrations and noise.

BRIEF DESCRIPTION OF THE DRAWINGS

The above mentioned and other features and objects of this invention,and the manner of attaining them, will become more apparent and theinvention itself will be better understood by reference to the followingdescription of an embodiment of the invention taken in conjunction withthe accompanying drawings, wherein:

FIG. 1 is a sectional view of a compact rotary compressor in accordancewith the present invention.

FIG. 2 is an enlarged fragmentary view of the indicated portion of FIG.1.

FIG. 3 is a sectional view of the compression mechanism of thecompressor of FIG. 1 showing a first position.

FIG. 4 is a sectional view of the compression mechanism of thecompressor of FIG. 1 showing a second position.

FIG. 5 is a top plan view of the inner plate of the compressor.

FIG. 6 is a sectional view of the inner plate of FIG. 5 taken along line6-6.

Corresponding reference characters indicate corresponding partsthroughout the several views. Although the exemplification set outherein illustrates an embodiment of the invention, in one form, theembodiment disclosed below is not intended to be exhaustive or to beconstrued as limiting the scope of the invention to the precise formdisclosed.

DESCRIPTION OF THE PRESENT INVENTION

Referring now to the drawings and particularly to FIG. 1, there is showna compact rotary compressor 10. Compressor 10 has hermetically sealedhousing 12 including base 14 and body portion 16 which are hermeticallysealed by welding, brazing, or the like at location 18. The size of base14 is greater than the diameter of cylindrical body portion 16 toprovide flange 20 having apertures 22 therein for mounting compressor10. Compressor 10 is illustrated as being in a substantially horizontalorientation however, compressors in accordance with the presentinvention may also be vertically orientated.

Compressor 10 includes electric motor 24 having stator 26 and rotor 28which defines a portion of compression mechanism 30 provided forcompressing refrigerant from a low pressure to a higher pressure for usein a refrigeration system, for example. Stator 26, having coil assembly32, is rigidly mounted and circumscribes rotor 28. Extending throughrotor 28 is stationary shaft 34 which is fixedly mounted at end 36 inaperture 38 centrally formed in body portion 16 of housing 12 bywelding, brazing, or the like (FIGS. 1 and 2). In the illustratedembodiment, weld 40 secures shaft 34 to housing 12.

Referring to FIGS. 3 and 4, a plurality of pockets 41 are formed in theouter radial surface of rotor 28 in which permanent magnets 42 aremounted by any suitable method including the use of adhesives, forexample. Rotor 28 is circumscribed by lamination stack 44 of stator 26(FIG. 1) and, during operation of compressor 10, stator 26 generates arotating electromagnetic field to rotationally drive rotor 28 havingpermanent magnets 42 mounted thereon. Rotor 28 also defines an internalcompression chamber 52. In the illustrated embodiment, rotor 28 isintegrally formed from a solid metal material such as steel, powdermetal, ductile iron, or the like in the general shape of an annularring. The rotor may be manufactured using any suitable method includingelectric discharge machining (EDM). By using a solid integral part toform rotor 28, no lining is required for internal compression chamber 52and the rotor may also include an integral vane 54 that extends radiallyinwardly within compression chamber 52 to engage roller 50 as discussedin greater detail below.

Stationary shaft 34 is formed from any suitable metal material includingsteel, powder metal, ductile iron, or the like by any conventionalmethod including machining, for example. Referring to FIG. 1, aneccentric portion 48 is integrally formed on shaft 34 and is locatedwithin compression chamber 52 defined by rotor 28. Roller 50 forms apart of compression mechanism 30 and is rotatably mounted on eccentric48. Referring to FIGS. 3 and 4, vane 54 is integrally formed with rotor28 and extends radially inwardly from the inner radial surface of rotor28 that defines compression chamber 52. Vane 54 engages roller 50 and,together with roller 50 divides compression chamber 52 intovariable-volume, crescent shaped compression pockets 56.

Referring to FIGS. 3 and 4, in order to allow for the relative slidingmovement between vane 54 which extends radially inwardly from cylinderblock portion 46 of rotor 28 and roller 50, roller 50 is provided withcylindrical aperture 58 extending longitudinally through roller 50adjacent the outer periphery thereof and defining an opening in theouter radial surface of roller 50. Guide bushing 60 is mounted inaperture 58 and has a longitudinally extending slot 62 formed therein toslidably receive vane 54 such that as rotor 28 rotates, vane 54reciprocatingly slides within slot 62 as roller 50 rotates on eccentricportion 48 and moves toward and away from the compression chamber walladjacent vane 54. Bushing 60 may also rotate within aperture 58 to allowfor change in angular position of vane 54 with respect to aperture 58 asrotor 24 and roller 50 are rotated. Similarly, aperture 58 has aradially outer opening that is sufficiently larget to allow for thisrelative angular movement of vane 54 during operation of the compressor.In the illustrated embodiment, bushing 60 is a two piece bushing,however, alternative embodiments may employ a single piece bushingwherein an interconnecting web of material extends between the twohalves of the bushing through a portion of space 130 and is sufficientlythin to avoid interfering with the reciprocation of vane 54 within slot62.

Guide bushing 60 is made from a material with suitable antifrictionproperties. In the illustrated embodiment, bushing 60 is formed usingVespel SP-21, a material commercially available from E.I. du Pont deNemours and Company, and which facililtates the reduction of frictionallosses caused by sliding movement of vane 54 in slot 62 and relativeoscillating movement of bushing 60 within aperture 58 of roller 50. Theuse of a guide bushing 60 from a material with good antifrictionproperties facilitates the reduction of wear of the surfaces of roller50, vane 54, and guide bushing 60 that are in moving contact to therebyimprove the longevity and reliability of the compressor.

As discussed above, vane 54 is integrally formed with the cylinder blockportion 46 of rotor 28 and the use of bushing 60 together with such anintegrally formed vane, eliminates the need for a vane spring to pressthe vane against the roller. The use of bushing 60 to slidably receivevane 54 instead of a spring biased vane, may also reduce the frictionalresistance to created by the vane during operation of the compressor.The relatively minimal frictional losses caused by vane 54 facilitatesthe minimization of power losses due to friction. The use of an integralvane that is slidably received within bushing 60 also facilitates thereduction of refrigerant vapor leakage across the barrier formed by vane54 between a relatively high pressure compression pocket to a relativelylow pressure compression pocket during operation of the compressor. Thereduced frictional losses and refrigerant leakage facilitate theefficient and reliable operation of the compressor. The use of anintegral vane 54 also facilitates the reduction of parts needed tomanufacture compressor 10 thereby simplifying and facilitating the costefficient manufacture of compressor 10.

Referring to FIGS. 1, 5, and 6, compression mechanism 30 also includesinner plate 64 is located in adjacent contact with upper axial endsurface 66 of rotor 28 to partially define and seal compression chamber52. As shown in FIGS. 5 and 6, a plurality of fluid passages are formedin inner plate 64 to define a portion of the discharge line which isfurther described below. Inner plate 64 is provided with centralaperture 68 through which shaft 34 extends. Positioned in adjacentcontact with the opposite surface of inner plate 64 is outer plate 70also having a central aperture 72 through which shaft 34 extends.Together plates 64 and 70 define a first end plate assembly. Althoughthe illustrated embodiment employs two plates, i.e., plates 64, 70 todefine the first end plate, the first end plate is not limited to a twopiece construction. Second end plate 74 is positioned in adjacentcontact with the lower axial end surface 76 of rotor 28 and partiallydefines and seals compression chamber 52. Cylindrical protrusion 78extends outwardly from the lower surface of plate 74 and is received inupstanding member 80. Second end plate is rotatably mounted on thestationary support defined by member 80 via bearing 88. A thrust bearing89 is also located between member 80 and second plate 74. The first endplate, i.e., inner plate 64 and outer plate 70, rotor 28 and secondplate 74 are secured together to define compression chamber 52. In theillustrated embodiment, a plurality of bolts extend through apertures inouter plate 70, inner plate 64, rotor 28, and second end plate 74 tosecure these components to one another. Alternative embodiments mayemploy alternative methods of securing these components together such aswelding.

Compression assembly 30 is rotatably mounted on shaft 34 by a pluralityof bearings 82, 84, and 86 which are press-fit into the aperturesdefined by outer plate 70 and inner plate 64, and the inner diameter ofroller 50, respectively. Bearing 88 is press-fit onto protrusion 78 torotatably support second end plate 74 by rotatably mounting protrusion78 in upstanding member 80. When the compressor is operating and rotor28 is rotated, bearings 82, 84, 86, and 88 rotatably support compressionassembly 30 as it is rotatably driven about stationary shaft 34. As bestseen in FIGS. 1, 3 and 4, bearings 82, 84 and 88 which rotatably supportrotor 24 and the first and second end plates enclosing compressionchamber 52 are centered on rotor axis 24 a and bearing 86 rotatablysupporting roller 50 is centered on roller axis 50 a defined byeccentric portion 48 of shaft 34. Axes 24 a and 50 a are spaced apartwhereby roller 50 will form a line, or area, of contact with the innerradial surface of rotor 24 that defines compression chamber 52 thatprogressively travels along the circumference of the inner radialsurface of rotor 24 as rotor 24 and roller 50 rotate about theirrespective axes. The relative rotation of rotor 24 and compressionchamber 52 and roller 50 with respect to shaft 34 and axes 24 a and 50 adefines compression pockets for compressing refrigerant in a mannertypical for rotary compressors that is well known in the art.

Bearings 82, 84, 86, 88 and 89 may be formed from a polyamide materialhaving relatively low coefficients of static and kinetic friction suchas Vespel SP-21. Another beneficial characteristic associated withpolyamide is that it demonstrates thermal stability over a relativelybroad temperature range. For example, polyamide bushings may be capableof withstanding a bearing pressure of approximately 300,000 lb ft/in²and a contact temperature of 740° F. For the optimum performance of thebushings and to avoid overheating, bushings 82, 84, 86 and 88advantageously have a length to inside diameter ratio of no more than3:2.

Compressor 10 as described above utilizes a bushing 60 and bearings 82,84, 86 and 88 that do not require lubrication. While the above-describedembodiment is equipped with self-lubricating bushings and bearings,alternative embodiments may utilize alternative bushings and bearings,e.g., needle or ball-type bearings and a conventional oil sump and pumpfor supplying lubricating oil to the bearings.

Assembly of compressor 10 may advantageously include first assemblingcompression assembly 30. Initially, roller 50, having guide bushing 60press fit therein is located in compression space 52 such that vane 54engages slot 62 and rotor 28 is positioned in abutting contact withsecond end plate 74. Bushing 86 is press fit within cylindrical aperture58 of roller 50 and shaft 34 is inserted within bushing 86 to therebyrotationally engage roller 50 and shaft 34. Inner plate 64 and outerplate 70, having the respective bearings 82 and 84 assembled therewith,are then positioned on shaft 34 and fasteners are used to secure thecompression chamber components together. Also mounted to shaft 34 iscompression kit 89 (FIGS. 1 and 2) which is provided to secure therelative position of compression mechanism 30 with respect to housing 12and stator 26. Compression kit 89 axially biases compression mechanism30 towards upstanding member 80. Compression kit 89 is shown in FIG. 2and includes wave spring 90 which applies pressure to steel washer 92facing upper surface 94 of bearing 82. Retaining ring 96 is located onthe opposite side of wave spring 90 and has a radially inner portion 97that engages annular groove 99 formed in shaft 34. Suitable wave springsare commercially available from the Smalley Steel Ring Company locatedin Lake Zurich, Ill. The assembled compression mechanism 30 is thenmounted in housing body portion 16 with end 36 of shaft 34 extendingthrough aperture 38. Shaft 34 is secured to body portion 16 of housing12 with weld 40. Also located in housing body portion 16 is inlet 98through which suction pressure refrigerant enters motor cavity 100.Stator 26 is shrink fitted into housing body portion 16 and iselectrically coupled via wire 102 to terminal assembly 104 also mountedin the housing body portion 16. Compression mechanism 30 is positionedwithin housing body portion 16 such that rotor 28 is aligned with stator26. The assembled compression mechanism and housing body portion is thenmounted to housing base 14 with bearing 88 mounted on protrusion 78being received in upstanding portion 80. Housing body portion 16 is thenwelded to housing base 14 at seam 18. By positioning compression chamber52 within rotor 24 and circumscribing rotor 24, compression chamber 52and end plates 64, 70 and 74 with stator 26 the overall assembled axialextending length of compressor 10 is relatively limited and therebyprovides a compact overall design that facilitates the flexiblepositioning of the compressor.

The compact arrangement provided by the present invention allows theaxial length of the compressor to be reduced to approximately the sameaxial length of the stator 26.

During compressor operation, electrical current supplied to stator 26via terminal assembly 104 creates a magnetic flux which in turn causesrotation of rotor 28. The rotation of rotor 28 drives the rotation ofroller 50 about drive shaft 34 through vane 54 which is integrallyformed with rotor 28 and engaged with roller 50. Referring to FIGS. 3and 4, as rotor 28 and roller 50 rotate, vane 54 slides within slot 62in bushing 60 and the crescent shaped compression pockets 56 definedwithin compression chamber 52 become progressively smaller as theyapproach discharge port 140. After passing discharge port 140,compression pockets 56 enlarge and refrigerant is drawn into thecompression pockets 56 through a suction port (not shown).

The refrigerant flows through a pathway best seen in FIGS. 1, 5, and 6.The pathway is partially defined by a plurality of passages located ininner plate 64 and provides for the intake and discharge of refrigerantfluid by compression mechanism 30. Relatively low pressure refrigerantvapor, i.e., suction pressure refrigerant, is introduced into the motorcavity 100 through inlet 98. Thus, compressor 10 is a low sidecompressor in which motor cavity 100 is filled with suction pressurerefrigerant. The suction pressure refrigerant is at a lower temperaturethan the compressed refrigerant and facilitates the cooling of themotor. The present invention is not limited to low side compressors,however, and alternative embodiments may employ a variety ofconfigurations including high side compressor designs wherein the motorcavity is filled with discharge pressure refrigerant.

In the illustrated embodiment, the refrigerant passes through a suctionport (not shown) in inner plate 64 and is introduced into a relativelylarge compression pocket 56 defined within compression chamber 52. Thesuction port is located in inner plate 64 such that discharge valve 106and the suction port are in communication with separate compressionpockets 56 throughout an entire 360 degree rotation of rotor 28 androller 50 about shaft 34. After refrigerant is drawn into a compressionpocket 56, rotation of rotor 28 and roller 50 about shaft 34 causes theprogressive reduction in size of the compression pocket and thecompression of the refrigerant vapor disposed therein, when thecompression pocket is in fluid communication with discharge valveassembly 106 and the pressure within the compression pocket issufficient to open the discharge valve assembly 106, compressedrefrigerant is discharged from compression chamber 52 through dischargeport 140 and the discharge valve assembly 106 disposed within dischargevalve cavity 12 formed in plate 64 as best seen with reference to FIGS.1, 5 and 6.

The discharge valve assembly includes a valve seat body 142 definingdischarge port 140 in fluid communication with compression chamber 52and a spherical valve member 144 biased into engagement with a valveseat defined by body 142 by spring 146 to thereby seal the dischargeport. A retaining ring 148 secures spring 146 within valve seat body142. When the fluid pressure within the discharge pocket 56 that is influid communication with the discharge port 140 exceeds the pressurenecessary to overcome the biasing force of spring 146, the valve will beforced open and refrigerant will be discharged from compression chamber52 through discharge port 140. The discharged refrigerant is thencommunicated through discharge cavity 112 to fluid channel 110. Fluidchannel 110 defines a passageway to the circular channel formingdischarge muffler 108. Discharge muffler 108, and passages 110 and 120,are defined by recesses in inner plate 64 and the sealing engagement ofouter plate 70 with inner plate 64 as best seen in FIG. 1. Muffler 108has two branches 116 and 118 (FIG. 5) each leading to channel 120 whichis in continuous fluid communication with peripheral groove 122 (FIG. 1)on shaft 34. Groove 122 is, in turn, in fluid communication with one ormore radial channels 124 formed in shaft 34. As best seen in FIG. 1,radial channel 124 communicates discharged refrigerant to passage 126extending longitudinally through shaft 34 toward discharge fitting 128.The compressed refrigerant is discharged from compressor 10 throughdischarge fitting 128 to a system that utilizes compressed fluid such asa refrigeration system or heat pump system.

The configuration of discharge muffler passage 108 helps to controlnoise and reduces the flow velocity. By providing a greater crosssectional area than the discharge port and channel 110, passage 108reduces the flow velocity of the discharged fluid which facilitates thereduction of noise. Additionally, during operation of the illustratedcompressor, compressed refrigerant vapors are discharged through valve106 on a periodic basis as the individual compression pockets 56 reachthe necessary pressure to open valve 106. The periodic discharge ofvapors through valve 106 may create a pressure wave within thedischarged vapors. By splitting the discharge flow into two separatechannels, i.e., branches 116 and 118, which then meet before thecompressed fluid enters radial channel 120, the pressure waves presentin the two separate channels meet and, if they are out of phase, atleast partially destructively interfere with each other, therebyreducing the amplitude of the pressure wave and the vibrations andresulting noise that may be created thereby. By altering the respectivelengths of branches 116 and 118 the wavelength of the pressure wavessubject to the most destructive interference can also be altered. In theillustrated embodiment, channel 120 is located diametrically oppositechannel 110 and branches 116 and 118 have similar lengths, however, inalternative embodiments, it may be advantageous to locate channel 120such that branches 116 and 118 have unequal lengths to enhance thedestructive interference of pressure waves having a selected wavelength.Dashed lines in FIG. 5 illustrate an alternative location 120 a for achannel providing communication between passage 108 and groove 122 thatdefines branches having unequal lengths. As described above, passage 108acts as a noise attenuation chamber by both reducing the velocity of thedischarged refrigerant conveyed therethrough and by promoting thedestructive interference of the pressure waves conveyed by thedischarged refrigerant.

Referring to FIGS. 3 and 4, the radial slot 62 in roller 50 has a smallspace 130 located between the distal end 132 of vane 54 and the surfaceof the roller 50 opposite distal end 132. As vane 54 reciprocates withinslot 62, the volume of space 130 is alternatively reduced and expanded.If space 130 is well sealed and without an outlet, the vapor withinspace 130 would be compressed as vane 54 moves further into slot 62 andexpanded as vane 54 move radially ouwardly within slot 62 therebyperforming work on the gas located in space 130 without obtaining anybenefit therefrom and degrading the efficiency of compressor 10. Ifspace 130 is not well sealed with respect to the compression pockets 56located on opposite sides of vane 54, as vane 54 moves radiallyoutwardly within slot 62, vapor from the relatively high pressureadjacent compression pocket might be drawn into space 130 and thenexpelled to the relatively low pressure adjacent compression pocket asvane 54 subsequently moves further into slot 62 thereby leading to thereexpansion of the vapor, loss of volumetric efficiency and a possibleincrease in undesirable noise.

To inhibit the loss of efficiency and reverse flow as a result of theinteraction of vane 54 and slot 62, bushing 60 engages opposite sides ofvane 54 and a communication passage 134 (FIGS. 1, 5, and 6) is formed inthe inner plate 64 to connect space 130 with the discharge mufflerpassage 108. Thus, as vane 54 moves further into slot 62, vapors withinspace 130 may be communicated to passage 108 and, as vane 54 movesradially outwardly within slot 62, vapor at discharge pressure may becommunicated to space 130 through passage 134.

While this invention has been described as having an exemplary design,the present invention may be further modified within the spirit andscope of this disclosure. This application is therefore intended tocover any variations, uses, or adaptations of the invention using itsgeneral principles.

1. A rotary compressor for compressing a fluid comprising: a motorhaving a stator and a rotor; wherein said rotor includes an integrallyformed part defining an internal compression chamber and an integrallyformed vane extending radially inwardly within said compression chamber;and a roller rotatably mounted and eccentrically disposed within saidcompression chamber, said vane engaged with said roller wherein rotationof said rotor rotates said roller and thereby compresses the fluidwithin said compression chamber.
 2. The rotary compressor of claim 1wherein said integrally formed part includes a radially outer surfacehaving a plurality of permanent magnets mounted thereon.
 3. The rotarycompressor of claim 1 wherein said roller defines a recess having abushing mounted therein, said bushing defining a radially extendingslot, said vane being slidably disposed within said slot.
 4. The rotarycompressor of claim 1 further comprising first and second end platesdisposed at opposite axial ends of said compression chamber.
 5. Therotary compressor of claim 1 wherein said roller is mounted on astationary shaft, said shaft defining an internal passageway in fluidcommunication with said compression chamber.
 6. The rotary compressor ofclaim 5 wherein at least one of said end plates defines a fluidpassageway providing fluid communication between said internalpassageway of said shaft and said compression chamber.
 7. The rotarycompressor of claim 1 further comprising first and second end platesdisposed at opposite ends of said compression chamber and wherein saidroller is mounted on a stationary shaft, said shaft extending through atleast one of said end plates.
 8. The rotary compressor of claim 7wherein said shaft extends through only said first end plate and saidsecond end plate is rotatably mounted on a stationary support structure.9. The rotary compressor of claim 1 further comprising first and secondend plates disposed at opposite ends of said compression chamber andwherein said stator circumscribes said rotor, said compression chamberdisposed therein and said first and second end plates.
 10. The rotarycompressor of claim 1 further comprising at least one end plate disposedat an end of said compression chamber, said at least one end platedefining a discharge fluid line having a discharge valve cavity in fluidcommunication with said compression chamber; said at least one end plateincluding a discharge valve member disposed within said discharge valvecavity and controlling fluid flow from said compression chamber throughsaid discharge valve cavity.
 11. The rotary compressor of claim 10wherein said end plate further defines a noise attenuation chamber influid communication with said discharge fluid line.
 12. A rotarycompressor for compressing a fluid comprising: a housing; a motormounted in said housing, said motor having a stator and a rotor, saidstator circumscribing said rotor, said rotor defining a rotational axisand including an integrally formed part defining an internal compressionchamber and an integrally formed vane extending radially inwardly withinsaid compression chamber, opposite axial ends of said rotor definingfirst and second rotor faces respectively; a first end plate secured tosaid first rotor face; a second end plate secured to said second rotorface; a stationary drive shaft mounted in said housing and extendingthrough at least one of said end plates and at least partially disposedwithin said compression chamber; and a roller rotatably mounted on saiddrive shaft wherein said roller is rotatable about an axis spaced fromthe rotational axis of said rotor, said vane engaged with said rollerwherein rotation of said rotor rotates said roller and therebycompresses the fluid within said compression chamber.
 13. The rotarycompressor of claim 12 wherein said integrally formed part includes aradially outer surface having a plurality of permanent magnets mountedthereon.
 14. The rotary compressor of claim 12 wherein said rollerdefines a recess having a bushing mounted therein, said bushing defininga radially extending slot, said vane being slidably disposed within saidslot.
 15. The rotary compressor of claim 12 wherein said shaft definesan internal passageway in fluid communication with said compressionchamber.
 16. The rotary compressor of claim 15 wherein at least one ofsaid end plates defines a fluid passageway providing fluid communicationbetween said internal passageway of said shaft and said compressionchamber.
 17. The rotary compressor of claim 12 wherein said shaftextends through only said first end plate and said second end plate isrotatably mounted on a stationary support structure.
 18. The rotarycompressor of claim 12 wherein said stator circumscribes saidcompression chamber disposed within said rotor and said first and secondend plates.
 19. The rotary compressor of claim 12 wherein said first endplate defines a discharge fluid line having a discharge valve cavity influid communication with said compression chamber; said first end plateincluding a discharge valve member disposed within said discharge valvecavity and controlling fluid flow from said compression chamber throughsaid discharge valve cavity.
 20. The rotary compressor of claim 19wherein said first end plate further defines a noise attenuation chamberin fluid communication with said discharge fluid line.